WO2011080924A1 - ベーン型圧縮機の潤滑オイル供給構造 - Google Patents
ベーン型圧縮機の潤滑オイル供給構造 Download PDFInfo
- Publication number
- WO2011080924A1 WO2011080924A1 PCT/JP2010/007589 JP2010007589W WO2011080924A1 WO 2011080924 A1 WO2011080924 A1 WO 2011080924A1 JP 2010007589 W JP2010007589 W JP 2010007589W WO 2011080924 A1 WO2011080924 A1 WO 2011080924A1
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- WIPO (PCT)
- Prior art keywords
- pressure chamber
- vane
- back pressure
- lubricating oil
- recess
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
- F04C18/3441—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/08—Rotary pistons
- F01C21/0809—Construction of vanes or vane holders
- F01C21/0818—Vane tracking; control therefor
- F01C21/0854—Vane tracking; control therefor by fluid means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
- F04C29/021—Control systems for the circulation of the lubricant
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
- F04C29/028—Means for improving or restricting lubricant flow
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/20—Rotors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/50—Bearings
- F04C2240/52—Bearings for assemblies with supports on both sides
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/50—Bearings
- F04C2240/56—Bearing bushings or details thereof
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/60—Shafts
- F04C2240/605—Shaft sleeves or details thereof
Definitions
- the present invention relates to a vane compressor mounted on an air conditioner such as a vehicle air conditioner, and more particularly to a structure for supplying lubricating oil to a bearing for supporting a drive shaft of the vane compressor.
- a vane type compressor In this type of vane type compressor, a cylinder closed by sandwiching both sides with a block, a rotor housed rotatably in the cylinder, and sliding in a plurality of vane grooves formed in the rotor.
- a vane and a drive shaft that is connected to the rotor and transmits a rotational force from the outside to the rotor.
- the drive shaft is supported by the both blocks via bearings, and
- a vane type compressor having a structure in which a plain bearing is used as a type of bearing is already known as disclosed in Patent Document 1, for example.
- the oil reservoir chamber is provided in the vicinity of one side in the axial direction of the drive shaft, and the oil passes through the oil supply passage from the oil reservoir chamber to the drive shaft.
- the oil from the oil reservoir chamber is supplied to both sliding bearings without unevenness. Otherwise, there is a concern that any of the sliding bearings will be insufficiently lubricated and abnormal noise and wear of the sliding bearing will easily occur.
- the present invention uses a back pressure chamber of a rotor having an existing structure, and is only a slight change in the shape of the recess formed on the cylinder side end surface of the block that closes the cylinder, and is far from the oil reservoir chamber. It is an object of the present invention to provide a lubricating oil supply structure for a vane compressor that can supply sufficient lubricating oil to a sliding bearing.
- a lubricating oil supply structure for a vane compressor includes a cylinder closed on both sides by a block, a rotor housed in the cylinder and formed with a plurality of vane grooves, and a vane groove in the rotor.
- a vane whose side surface slides on the inner side surface of the vane groove and whose tip protrudes and retracts from the vane groove and slides on the inner peripheral surface of the cylinder, and a spine formed at the bottom of the vane groove.
- the lubricating oil enters from the oil reservoir chamber between the drive shaft and one of the blocks, and flows along the axial direction of the drive shaft. Then, after lubricating one of the bearings located in the middle, the first recess formed in the cylinder side end surface of the one block, the back pressure chamber, and the cylinder side end surface of the other block of the block are formed.
- Lubricating oil that flows in the order of the second recesses, enters between the drive shaft and the other block, flows again along the axial direction of the drive shaft, and lubricates the other bearing located in the middle thereof
- the first concave portion and the second concave portion each have a path, and each change a communication state with the back pressure chamber as the position of the back pressure chamber varies due to rotation of the rotor.
- the change in the state of communication with the back pressure chamber and the time when the amount of stroke of the vane increases Link before By relatively lower than the surrounding pressure in the back pressure chamber, it is characterized in that as the lubricating oil is supplied to the back pressure chamber (claim 1).
- the bearing is a sliding bearing such as a plain bearing, the effects of the present invention can be enjoyed more effectively.
- the cylinder is closed on both sides by a block integral with the cylinder and a block separate from the cylinder, both sides are closed by blocks separate from the cylinder. Also good.
- the change in the communication state with the back pressure chamber includes opening / closing of the communication state with the back pressure chamber and expansion / reduction of the communication region with the back pressure chamber. The same applies to the following vane type compressors.
- the flow rate of the lubricating oil when it is sent from the back pressure chamber to the gap between the block that closes the drive shaft and the cylinder is the other block of the block that closes the drive shaft and the cylinder.
- the open / close state of the communication with the back pressure chamber and the communication area By setting the expansion / contraction, the flow rate of the lubricating oil delivered from the back pressure chamber to the gap between the drive shaft and the other block among the blocks closing the cylinder increases in accordance with the difference.
- the lubricating oil supply structure of the vane type compressor according to the second aspect of the invention includes a timing when the space between the first recess and the back pressure chamber is opened, the second recess and the back.
- a shift occurs between the first recess and the back pressure chamber, and between the second recess and the back pressure chamber.
- lubricating oil is supplied to the back pressure chamber by linking the deviation and the timing when the stroke amount of the vane increases. More specifically, when the stroke amount of the vane increases, the interval between the first recess and the back pressure chamber is opened earlier than between the second recess and the back pressure chamber. (Claim 3).
- the lubricating oil supply structure for a vane compressor includes a cylinder closed on both sides by a block, a rotor housed in the cylinder and formed with a plurality of vane grooves, and a vane of the rotor
- the vane is housed in the groove, and the side surface slides on the inner surface of the vane groove, and the tip of the vane slides on the inner peripheral surface of the cylinder with the tip protruding and retracting from the vane groove.
- a back pressure chamber a drive shaft that is supported by the block via bearings and is connected to the rotor and transmits a rotational force from the outside to the rotor, and an oil reservoir chamber in which lubricating oil is temporarily stored
- the lubricating oil enters from the oil reservoir chamber between the drive shaft and one of the blocks, and follows the axial direction of the drive shaft. And lubricate one of the bearings located in the middle of the first concave portion formed in the cylinder side end surface of the one block, the back pressure chamber, and the cylinder side end surface of the other block of the block.
- the lubricating oil supply structure of the vane type compressor according to the invention of claim 5 includes a timing when the space between the first recess and the back pressure chamber is closed, the second recess and the back pressure. A gap between the first recess and the back pressure chamber and between the second recess and the back pressure chamber. Lubricating oil is sent out from the back pressure chamber by linking the deviation with the timing when the stroke amount of the vane decreases. More specifically, when the stroke amount of the vane decreases, the gap between the first recess and the back pressure chamber is closed earlier than between the second recess and the back pressure chamber. (6).
- the driving shaft is divided into a portion having a relatively deep depth in the axial direction and a portion having a relatively shallow depth, and the communication state with the back pressure chamber is changed using the difference in depth.
- the depth of the entire region of the first concave portion or the second concave portion which is not classified into a relatively deep portion and a relatively shallow portion in the axial direction of the drive shaft is the depth of the entire region.
- the depth of the relatively deep part of the concave part divided into a shallow part and a narrow part is the same (claim 8).
- the lubricating oil is mainly fed into the back pressure chamber from the first concave portion side, and the lubricating oil is similarly sent from the back pressure chamber to both the first concave portion and the second concave portion.
- the flow rate of the lubricating oil when it is sent to the gap with the other block among the blocks to be moved is when it is fed into the back pressure chamber through the gap between the block that blocks the drive shaft and the cylinder. From the back pressure chamber to the drive shaft and cylinder The flow rate of lubricating oil to be delivered to the gap between the other blocks of the blocks that closes increases with the difference.
- the flow rate of the lubricating oil that is sent from the back pressure chamber to the gap between the block that blocks the drive shaft and the cylinder blocks the drive shaft and the cylinder.
- the first recess and the second recess with respect to the back pressure chamber so that the flow rate of the lubricating oil is larger than the flow rate of the lubricating oil when it is fed into the back pressure chamber from the gap with the other blocks of the blocks to be Set the open / close of the communication state and expansion / contraction of the communication area according to the timing of increase / decrease of the stroke amount of the vane, and send it from the back pressure chamber to the gap between the block that blocks the drive shaft and the cylinder
- the flow rate of the lubricating oil can be increased according to the difference.
- the lubricating oil is surely and sufficiently supplied to the other bearing located farther from the oil reservoir than one bearing. Can be supplied in quantity. Therefore, it is possible to suppress the occurrence of noise or wear in the other bearing due to the lack of lubricating oil with respect to the other bearing, thereby improving the durability of the bearing and thus the vane compressor. It becomes possible.
- the stroke amount of the vane increases, the volume of the back pressure chamber at the bottom of the vane groove increases, and the pressure in the back pressure chamber increases. Therefore, when the timing when only the first recess is opened and the timing when the stroke of the vane increases, the first recess is removed from the oil reservoir chamber for the lubricating oil. It can be supplied to the back pressure chamber.
- the lubricating oil is mainly fed into the back pressure chamber from the first recessed portion side, and the first recessed portion and the second recessed portion are fed from the back pressure chamber.
- the lubricating oil is sent to both sides, and the lubricating oil is mainly fed into the back pressure chamber from the first concave portion side, and the lubricating oil is mainly fed from the back pressure chamber to the second concave portion.
- a pattern in which the lubricating oil is similarly fed into the back pressure chamber from both concave portions, and the lubricating oil is mainly fed from the back pressure chamber to the second concave portion.
- the flow rate of the lubricating oil when it is sent from the back pressure chamber to the gap between the block that blocks the drive shaft and the cylinder is the other block of the block that blocks the drive shaft and the cylinder.
- the flow rate of the lubricating oil when it is fed into the back pressure chamber from the clearance between the drive shaft and the other block among the blocks that block the cylinder is sent from the back pressure chamber.
- the flow rate of the lubricating oil increases according to the difference. As a result, it is possible to suppress the occurrence of abnormal noise or wear in the other bearing due to the lack of lubricating oil for the other bearing, and to improve the durability of the bearing and thus the vane compressor. Is possible. *
- FIG. 1 is a cross-sectional view showing the overall configuration of a vane compressor according to the present invention.
- FIG. 2 shows the state of the front block in the axial direction of the drive shaft constituting the vane type compressor according to the first embodiment of the present invention when the side having the second recess is viewed from the rear side. It is explanatory drawing which shows only the 1st recessed part of the block of the axial direction back of the drive shaft which comprises a vane type compressor with a broken line.
- FIG. 3 is an explanatory view showing a state in which the concave portion on the side having the oil reservoir chamber is opened earlier than the concave portion on the opposite side in Embodiment 1 of the present invention, and FIG. FIG.
- FIG. 3B is a cross-sectional view of the drive shaft cut in the radial direction
- FIG. 3B is a cross-sectional view taken along line AA of FIG.
- FIG. 4 is an explanatory view showing a state in which both concave portions are opened in Embodiment 1 of the present invention
- FIG. 4 (a) is a sectional view of the rotor cut in the radial direction of the drive shaft.
- FIG. 4B is a cross-sectional view taken along the line BB of FIG.
- FIG. 5 is an explanatory view showing a state in which the concave portion on the side having the oil reservoir chamber is not closed yet in FIG. 5 (a).
- FIG. 5 (a) shows the rotor in the radial direction of the drive shaft.
- FIG. 5B is a sectional view taken along the line CC in FIG. 5A.
- FIG. 6 is an explanatory view showing a state in which the concave portion on the side having the oil reservoir chamber is closed earlier than the concave portion on the opposite side in Embodiment 1 of the present invention
- FIG. FIG. 6B is a cross-sectional view taken along the radial direction of the drive shaft
- FIG. 6B is a cross-sectional view taken along the line DD of FIG.
- FIG. 7 is a cross-sectional view taken along the line XX of FIG. 1 for the vane type compression in the first example of the second embodiment of the present invention.
- FIG. 8 is a cross-sectional view taken along the line YY of FIG.
- FIG. 9 shows a case where lubricating oil is supplied to the back pressure chamber in the first example of Embodiment 2 of the present invention.
- FIG. 9A shows the rotor cut in the radial direction of the drive shaft.
- 9C is a cross-sectional view of the driven shaft viewed from the axial direction rearward of the drive shaft, and
- FIG. 9C is a cross-sectional view of the state of the rotor cut in the radial direction of the drive shaft viewed from the axial front of the drive shaft.
- FIG. 9B is a cross-sectional view taken along line EE of FIGS. 9A and 9C.
- FIG. 10 shows a case where the lubricating oil is delivered from the back pressure chamber in the first example of the second embodiment of the present invention.
- FIG. 10 (a) shows the rotor cut in the radial direction of the drive shaft.
- FIG. 10C is a cross-sectional view of the rotor as viewed from the front in the axial direction of the drive shaft, with the rotor cut in the radial direction of the drive shaft.
- FIG. 10B is a cross-sectional view taken along the line FF of FIGS. 10A and 10C.
- FIG. 11 shows a case where lubricating oil is supplied to the back pressure chamber in the second example of the second embodiment of the present invention.
- FIG. 11A shows the rotor cut in the radial direction of the drive shaft.
- FIG. 11C is a cross-sectional view of the rotor cut in the radial direction of the drive shaft as viewed from the front in the axial direction of the drive shaft.
- FIG. 11 (b) is a cross-sectional view taken along the line GG of FIGS. 11 (a) and 11 (c).
- FIG. 12 shows a case where lubricating oil is delivered from the back pressure chamber in the second example of the second embodiment of the present invention.
- FIG. 12 (a) shows the rotor cut in the radial direction of the drive shaft.
- FIG. 12C is a cross-sectional view of the rotor cut in the radial direction of the drive shaft as viewed from the front in the axial direction of the drive shaft.
- FIG. 12B is a cross-sectional view taken along the line HH of FIGS. 12A and 12C.
- FIG. 13 shows a case where lubricating oil is supplied to the back pressure chamber in the third example of Embodiment 2 of the present invention.
- FIG. 13 (a) shows the rotor cut in the radial direction of the drive shaft.
- FIG. 13C is a cross-sectional view of the rotor cut in the radial direction of the drive shaft as viewed from the front in the axial direction of the drive shaft.
- FIG. 13 (b) is a cross-sectional view taken along the line II of FIG. 13 (a) and FIG. 13 (c).
- FIG. 13 shows a case where lubricating oil is supplied to the back pressure chamber in the third example of Embodiment 2 of the present invention.
- FIG. 13 (a) shows the rotor cut in the radial direction of the drive shaft.
- FIG. 13C is a cross-sectional view of the rotor cut in
- FIG. 14 shows a case where lubricating oil is delivered from the back pressure chamber in the third example of Embodiment 2 of the present invention.
- FIG. 14 (a) shows the rotor cut in the radial direction of the drive shaft.
- 14C is a cross-sectional view of the driven shaft viewed from the rear in the axial direction of the drive shaft
- FIG. 14C is a cross-sectional view of the rotor cut in the radial direction of the drive shaft viewed from the front in the axial direction of the drive shaft.
- FIG. 14B is a cross-sectional view taken along line JJ of FIGS. 14A and 14C.
- FIG. 1 to 6 show the whole or a part of the configuration of an example of a vane type compressor 1 that can use the lubricating oil supply structure according to the present invention.
- This vane type compressor 1 is suitable for a refrigeration cycle using, for example, a refrigerant as a working fluid, and is used for a vehicle air conditioner or the like. Further, as shown in FIG. 1, the vane compressor 1 includes a drive shaft 2, a rotor 3 fixed to the drive shaft 2 and movable as the drive shaft 2 rotates, and the rotor 3. It has a block 5 and a block 6 that define a compression space 4 to be described later, and the block 5 and the block 6 constitute a housing that houses the drive shaft 2, the rotor 3, and the like. .
- the block 6 is a cylinder 6a for housing the rotor 3, and this cylinder 6a is located on the rear side in the axial direction of the drive shaft 2, and the rear side block 6b integrally formed with the cylinder 6a; Consists of.
- the cylinder 6a is opened to the block 5 side as shown in FIG. 3 (b), FIG. 4 (b), FIG. 5 (b) and FIG.
- the cylinder hole 6c is provided.
- the block 5 includes a front side block 5a that abuts a front side end face located in front of the drive shaft 2 in the axial direction of the cylinder 6a, and a cylinder 6a of the block 6 extending from the front side block 5a in the axial direction of the drive shaft 2. And a shell 5b surrounding the outer peripheral surface of the rear block 6b.
- the block 5 is connected to the block 6 via a connector 7 such as a bolt.
- a plurality of O-rings 11 are interposed between the shell 5b of the block 5 and the outer peripheral surfaces of the cylinder 6a and the rear side block 6b of the block 6 and are fixed with good airtightness.
- the block 5 is formed with a boss portion 5c extending from the front side block 5a along the axial direction of the drive shaft 2 to the opposite side of the shell 5b.
- a pulley (not shown) for transmitting the rotation is externally rotatably mounted, and rotational power is transmitted from the pulley to the drive shaft 2 via an electromagnetic clutch (not shown).
- the rotor 3 is rotatably accommodated in a cylinder hole 6c formed in the cylinder 6a of the block 6, and includes a rotor body 3a fixed to the drive shaft 2 and a plurality of (provided to the rotor body 3a ( In this embodiment, there are a plurality of (two in this embodiment) vanes 9 inserted into the two vane grooves 8.
- the vane groove 8 is opened not only in the cylinder hole 6c of the block 6, but also on the front side block 5a side of the block 5 and the rear side block 6b side of the block 6, and on the far side in the sliding direction of the vane 9.
- a back pressure chamber 10 is formed at the bottom.
- the back pressure chamber 10 is also opened to the front block 5 a side of the block 5 and the rear block 6 b side of the block 6.
- the vane 9 has a side surface that slides on the inner surface of the vane groove 8 and a tip that protrudes and protrudes from the vane groove 8 and slides on the inner peripheral surface of the cylinder 6a.
- the amount of protrusion of the vane 9 from the vane groove 8 is defined as the stroke amount.
- the drive shaft 2 is rotatably supported by the front side block 5a of the block 5 and the rear side block 6b of the block 6 via plain bearings 12 and 13, respectively.
- the bearings are not limited to the plain bearings 12 and 13 as long as the bearings require supply of lubricating oil.
- the drive shaft 2 has a seal member 14 interposed between the inner peripheral surface of the block 5 in the vicinity of the base end of the boss portion 5c of the block 5, and the working fluid is exposed to the outside from the opening of the boss portion 5c. Prevents leakage.
- the block 5 is formed with a suction port 16 and a discharge port 17 for the working fluid, and a space 18 is formed on the radially inner side of the drive shaft 2 with respect to the suction port 16.
- a suction space (low pressure space) 15 is defined by the space portion 18 and a hollow portion 22 formed in the cylinder 6a of the block 6 and opened to the block 5 side.
- a discharge space (high pressure space) 24 is defined by the cylinder 6 a of the block 6 and the shell 5 b of the block 5, and this discharge space 24 communicates with the discharge port 17.
- an oil separator 25 is disposed between the discharge space 24 and the discharge port 17, and the oil separated from the working fluid by the oil separator 25 is temporarily stored in an oil reservoir chamber 19 described later. .
- the rotor body 3a of the rotor 3 and the cylinder hole 6c of the cylinder 6a are viewed as a cross section in which the cylinder 6a is cut in the radial direction of the drive shaft 2 and the end face of the rotor body 3a faces the opening of the cylinder hole 6c, FIG. 3 (a), FIG. 4 (a), FIG. 5 (a) and FIG. 6 (a), the rotor body 3a has an axial center P1 of the cylinder hole 6c.
- the rotor body 3a is accommodated in the cylinder hole 6c so as to be displaced toward the suction port 16 and the discharge port 17 as compared with the center P2. This deviation is, for example, 1 ⁇ 2 of the difference between the inner diameter of the cylinder hole 6c and the outer diameter of the rotor body 3a.
- the outer peripheral surface of the rotor body 3a is in contact with the inner peripheral surface of the cylinder hole 6c at a predetermined distance in a predetermined range in a predetermined range, and the outer peripheral surface of the rotor body 3a and the cylinder hole 6c A compression space 4 is defined between the two. Further, the compression space 4 is divided into a plurality of compression chambers 21 by being partitioned by the vanes 9. The volume of each compression chamber 21 changes with the rotation of the rotor 3.
- a discharge port communicating with the discharge space 24 is provided on the inner peripheral surface of the cylinder hole 6c.
- both ends of the cylinder 6a are in the axial direction of the drive shaft 2 of the cylinder 6a between the outer peripheral surface of the cylinder 6a and the inner peripheral surface of the shell 5b.
- a discharge space 24 defined by flanges 26 and 27 projecting in the radial direction of the drive shaft 2 from both ends is formed, and the discharge space 24 can communicate with the compression space 4 through a discharge port.
- the discharge port is opened and closed by a discharge valve (not shown) accommodated in the discharge space 24.
- the operation of suction, compression, and discharge of the working fluid in the vane compressor 1 is as follows. That is, when rotational power from a power source (not shown) is transmitted to the drive shaft 2 via a pulley and an electromagnetic clutch and the rotor 3 rotates, the working fluid flowing into the suction space 15 from the suction port 16 passes through the suction port. Inhaled into the compression space 4. Since the volume of the compression chamber 21 partitioned by the vanes 9 in the compression space 4 changes according to the rotation of the rotor 3, the working fluid confined between the vanes 9 is compressed and is discharged from a discharge port (not shown). It discharges to the discharge space 24 through a discharge valve (not shown). The working fluid discharged into the discharge space 24 moves in the circumferential direction along the outer peripheral surface of the cylinder 6a. After that, oil is separated by the oil separator 25 and then discharged from the discharge port 17 to the external circuit.
- the vane compressor 1 further includes a lubricating oil supply structure for supplying the oil in the oil reservoir chamber 19 to the plain bearings 12 and 13 as a lubricant.
- a lubricating oil supply structure for supplying the oil in the oil reservoir chamber 19 to the plain bearings 12 and 13 as a lubricant.
- the oil reservoir chamber 19 is the starting point.
- a relay passage 30 connecting the drive shaft storage space 29 storing the drive shaft 2 in the rear side block 6b of the block 6 and the oil reservoir chamber 19 is provided.
- the rear block 6b of the block 6 is provided.
- the downstream opening of the relay passage 30 opens below the end of the drive shaft 2 of the drive shaft storage space 29 or below the end of the drive shaft 2.
- the drive shaft storage space 29 is a hole that extends along the axial direction of the drive shaft 2 in the rear side block 6b of the block 6 and extends along the axial direction. It is approximately equal to the outer diameter of the mounted state.
- the plain bearing 13 is mounted on the rear side block 6b in the main portion of the drive shaft storage space 29 that is in front of the opening of the relay passage 30.
- a drive shaft storage space 31 for storing the drive shaft 2 in the front side block 5a of the block 5.
- the drive shaft storage space 31 is a hole extending along the axial direction of the block 5 so as to surround the outer periphery of the drive shaft 2 and reaches the opening of the boss portion 5c.
- a seal chamber 32 for housing the member 14 is provided.
- the inner diameter dimension of the portion of the drive shaft housing space 31 behind the seal chamber 32 is substantially equal to the outer diameter dimension of the drive shaft 2 with the plain bearing 12 mounted.
- the plane bearing 12 is mounted on the front block 5a in the portion of the drive shaft storage space 31 that is behind the seal chamber 32.
- the plain bearings 12 and 13 are cylindrical, and the inner diameter is slightly larger than the outer diameter of the drive shaft 2. As a result, when the plain bearings 12 and 13 are mounted on the blocks 5 and 6, as shown in FIGS. 3B, 4B, 5B, and 6B, driving is performed. Lubricating oil supply passages 33 and 34 are formed in an annular shape between the outer peripheral surface of the shaft 2 and the inner peripheral surfaces of the plain bearings 12 and 13.
- the lubricating oil supply passages 33 and 34 are connected to the first and second recesses 36 and 37 and the back pressure chamber 10 defined on the bottom side of the vane groove 8 as will be described in detail later. It is possible to communicate with each other.
- the first recess 36 is located axially forward (rotor 3 side) of the drive shaft 2 relative to the plain bearing 13 with respect to the drive shaft storage space 29 provided in the rear side block 6 b of the block 6.
- the second recess 37 is formed so as to be continuous with the space 29, and is axially rearward of the drive shaft 2 with respect to the drive shaft storage space 31 provided in the front side block 5 a of the block 5 (in the axial direction of the drive shaft 2). It is located on the rotor 3 side) and is formed to be continuous with the drive shaft storage space 31.
- the first recess 36 and the second recess 37 are provided in the rear block 6 b of the block 6 or the front block 5 a of the block 5.
- first recess 36 and the second recess 37 have the same shape, and are in a positional relationship shifted from each other by rotating at a predetermined angle with the axis P1 of the drive shaft 2 as the rotation center. Accordingly, the shape of the second recess 37 will be described with reference to FIG. 2.
- the circular line L1 constituting the circular opening edge of the drive shaft storage space 31 is used as the inner edge as it is, and the drive is performed from the circular line L1.
- a communication state forming portion 37a that extends radially outward of the shaft 2 and that has a relatively large radial dimension of the drive shaft 2 and a communication state formation in which the radial dimension of the drive shaft 2 is smaller than the communication state forming portion 37a.
- the dimension of the arcuate line L2 forming the arcuate outer edge of the communication state forming portion 37a is, for example, substantially the same as the dimension of the bottom surface position of the vane 9 when the vane 9 has the minimum stroke amount.
- the dimension of the arcuate line L3 that forms the arcuate outer edge of the communication state non-corresponding portion 37b is smaller than the position of the back pressure chamber 10 on the drive shaft 2 side. That is, the dimension of the arc-shaped line L3 that forms the arc-shaped outer edge of the communication state formation non-corresponding portion 37b is a dimension that does not communicate with the back pressure chamber 10.
- both ends of the arcuate line L2 and both ends of the arcuate line L3 are connected by straight lines L4 and L5 extending radially from the axis P1 of the drive shaft 2 in this embodiment.
- the first concave portion 36 will also be described with reference to FIG. 2.
- the circular line L1 constituting the circular opening edge of the drive shaft storage space 29 is used as an inner edge as it is, and the circular line L1 is used to drive the drive shaft 2. While expanding radially outward, it has a shape having a communication state forming portion 36a and a communication state non-corresponding portion 36b.
- the dimension of the arcuate line L2 forming the arcuate outer edge of the communication state forming portion 36a is, for example, substantially the same as the dimension of the bottom surface position of the vane 9 when the vane 9 is at the minimum stroke amount.
- the dimension of the arcuate line L3 that forms the arcuate outer edge of the communication state formation non-corresponding portion 36b is smaller than the position of the back pressure chamber 10 on the drive shaft 2 side. That is, the dimension of the arcuate line L3 forming the arcuate outer edge of the communication state non-corresponding portion 36b is a dimension that does not communicate with the back pressure chamber 10. Furthermore, both ends of the arcuate line L2 and both ends of the arcuate line L3 of the communication state non-corresponding portion 36b are connected by two straight lines L4 and L5 extending radially from the axis P1 of the drive shaft 2 in this embodiment. Has been.
- a point X2 is provided in front of the rotor 3 in the rotation direction with respect to a point X1 that contacts the outer peripheral surface of the rotor body 3a of the rotor 3 and the inner peripheral surface of the cylinder hole 6c with a minimum clearance, and the tip of the vane 9 is set to X2.
- the straight line L5, S1 is set so that the back pressure chamber 10 at the bottom of the vane groove 8 becomes the boundary between the communication state forming part 36a and the communication state non-corresponding part 36b of the first recess 36.
- the positional relationship is set such that the boundary line S2 of the second recess is further shifted by a predetermined angle forward along the rotational direction of the rotor body 3a.
- the rotor body 3a rotates clockwise, and the back pressure chamber 10 of the vane 9 rotates clockwise about the axis P1 of the drive shaft 2 as a result.
- the first recess 36 communicates with the communication state forming part 36a, but the relationship with the second recess 37 does not correspond to the communication state formation.
- the extension line S2 is crossed so that both the first concave part 36 and the second concave part 37 are in the communication state forming parts 36a and 37a. It becomes a state of communication.
- the communication state forming portion of the second recess 37 Communicating with 37a, the 2nd crevice 37 will also be in an open state.
- a point X3 is provided on the rear side in the rotational direction of the rotor 3 with respect to the contact point X1 between the outer peripheral surface of the rotor body 3a of the rotor 3 and the inner peripheral surface of the cylinder hole 6c, and the tip of the vane 9 becomes X3.
- straight lines L4, S4 are arranged so that the back pressure chamber 10 at the bottom of the vane groove 8 becomes a boundary between the communication state forming part 37a and the communication state non-corresponding part 37b of the second recess 37.
- the positional relationship is set so that the boundary line S3 of the first recess is further shifted by a predetermined angle forward along the rotational direction of the rotor body 3a.
- the rotor body 3a rotates clockwise, and the back pressure chamber 10 of the vane 9 rotates clockwise about the axis P1 of the drive shaft 2 as a result.
- the state where the first concave portion 36 and the second concave portion 37 communicate with each other at the communication state forming portions 36a and 37a is maintained.
- the second recess 37 communicates with the communication state forming portion 37a, and the relationship with the first recess 36 does not correspond to the communication state formation.
- the stroke amount of the vane 9 located behind the contact point X1 is decreased. Is reduced, and the pressure in the back pressure chamber 10 is relatively increased compared to the surroundings. For this reason, at least the lubricating oil in the back pressure chamber 10 can surely reach the plain bearing 12 through the communication state forming portion 37 a of the second recess 37.
- FIGS. 7 to 14 show a part of the configuration of a plurality of examples of the embodiment 2 of the vane compressor 1 that can use the lubricating oil supply structure according to the present invention.
- the first example to the third example of the second embodiment of the vane compressor will be described with reference to FIGS. 7 to 14.
- the first concave portion 36 and the second concave portion 37, which are parts, are basically described, and the same reference numerals are given to the same components as those in the first embodiment, and the description thereof is omitted.
- (First example) 7 to 10 show a first example of the embodiment 2 of the vane type compressor 1 that can use the lubricating oil supply structure according to the present invention.
- the second recess 37 shown in the first example of the second embodiment is provided in the front side block 5a of the block 5, and is provided in the drive shaft storage space 31 provided in the front side block 5a of the block 5. On the other hand, it is located behind the plain bearing 13 in the axial direction of the drive shaft 2 (on the rotor 3 side) and is formed to be continuous with the drive shaft storage space 31. Then, as shown in FIG. 7, the second recess 37 has a circular line L1 constituting the circular opening edge of the drive shaft storage space 31 as an inner edge, and is a circle concentric with the circular line L1.
- a shape line L6 is used as an outer edge, and the shape extends from the circular line L1 to the outside in the radial direction of the drive shaft 2 with the same dimensions throughout the entire circumference.
- the dimension of the circular line L6 that forms the circumferential outer edge of the second recess 37 is, for example, substantially the same as the dimension of the bottom surface position of the vane 9 at the time of the minimum stroke amount of the vane 9.
- the 2nd recessed part 37 has the recessed deep part 37c and the recessed shallow part 37d, as FIG.7, FIG.9 and FIG.10 shows.
- the recessed deep portion 37c and the recessed shallow portion 37d are formed with respect to the second recessed portion 37 with respect to the axis P1 of the rotor body 3a and the cylinder hole 6c. It is divided by two boundary lines S5 and S6 extending along a straight line passing through both of the centers P2, and the axial depth of the drive shaft of the recessed portion 37c is the axial direction of the drive shaft of the recessed shallow portion 37d. Is greater than the depth of.
- the communication area through which the lubricating oil passes through the second concave portion 37 is When it is relatively expanded and the opening on the front side block 5a side of the back pressure chamber 10 is in a range facing the concave shallow portion 37d of the second concave portion 37, the lubricating oil passes through the second concave portion 37.
- the communication area is relatively reduced.
- the first recess 36 shown in the first example of the second embodiment is provided in the rear side block 6b of the block 6, and with respect to the drive shaft storage space 29 provided in the rear side block 6b.
- the drive shaft 2 is positioned in front of the plain bearing 13 in the axial direction (on the rotor 3 side), and is formed so as to be continuous with the drive shaft storage space 29.
- the first recess 36 has a circular line L1 constituting the circular opening edge of the drive shaft storage space 29 as an inner edge, and is a circle that is concentric with the circular line L1.
- a shape line L6 is used as an outer edge, and the shape extends from the circular line L1 to the outside in the radial direction of the drive shaft 2 with the same dimensions throughout the entire circumference.
- the dimension of the circular line L6 that forms the circumferential outer edge of the first recess 36 is, for example, substantially the same as the dimension of the bottom surface position of the vane 9 when the vane 9 is at the minimum stroke amount.
- the first recess 36 is different from the second recess 37 in that the axial depth of the drive shaft is the same in the entire area as shown in FIGS. 9C and 10C. ing. Further, the depth dimension of the first recess 36 is the same as the axial depth of the drive shaft of the recess depth portion 37 c of the second recess 37. Thereby, even if the opening on the rear block 6b side of the back pressure chamber 10 is opposed to any range of the first recess 36, the communication area through which the lubricating oil passes through the first recess 36 is relatively expanded. It is in the state.
- the point where the boundary line S5 and the inner peripheral surface of the cylinder hole 6c intersect is defined as X5, and the boundary line S6 and the inner periphery of the cylinder hole 6c.
- the point where the plane intersects is X6, and the rotation direction of the rotor 3 is opposite to that shown in the arrows in FIGS. 9 (a) and 10 (a) when viewed from the front side of the vane compressor 1.
- X5 is the starting point.
- X6 is the end point, as indicated by the thick arrow in FIG.
- the pressure in the back pressure chamber 10 is relatively lower than the lubricating oil supply passages 33 and 34, and the back pressure chamber 10 is supplied with the lubricating oil from the lubricating oil supply passages 33 and 34. Since the back pressure chamber 10 communicates with the back pressure chamber 10 through a shallow shallow portion 37d, the communication area between the second recess 37 and the back pressure chamber 10 is relatively reduced.
- the volume of the back pressure chamber 10 is reduced by the vane 9 sliding in the vane groove 8 in the direction of decreasing the stroke amount,
- the second recess 37 Since the back pressure chamber 10 communicates with the recessed depth portion 37c, the communication area between the second recessed portion 37 and the back pressure chamber 10 is relatively enlarged.
- the flow rate of the lubricating oil sent from the lubricating oil supply passage 33 to the back pressure chamber 10 via the second recess 37 is the lubricating oil sent from the back pressure chamber 10 to the lubricating oil supply passage 33 via the second recess 37. Therefore, it is possible to increase the flow rate of the lubricating oil sent from the back pressure chamber 10 to the lubricating oil supply passage 33 when viewed comprehensively.
- (Second example) 11 and 12 show a second example of the second embodiment of the vane type compressor 1 that can use the lubricating oil supply structure according to the present invention.
- the second recess 37 shown in the second example of the second embodiment has the same configuration as that of the first example of the second embodiment described above, as shown in FIGS. 11 (a) and 12 (a).
- the first recess 36 shown in the second example of the second embodiment has a recessed deep portion 37c and a recessed shallow portion 37d. It is configured.
- symbol same as the 1st example of Example 2 is attached
- subjected the description is abbreviate
- the position of the first recess 36 in which the first recess 36 is provided is the same as that of the first example of the second embodiment, and a description thereof will be omitted.
- the first recess 36 has a circular line L1 constituting the circular opening edge of the drive shaft storage space 31 as an inner edge, and is concentric with the circular line L1.
- a circular line L6 is used as an outer edge, and the circular line L1 extends from the circular line L1 to the outer side in the radial direction of the drive shaft 2 with the same dimensions throughout the entire circumference.
- the dimension of the circular line L6 that forms the circumferential outer edge of the first recess 36 is, for example, substantially the same as the dimension of the bottom surface position of the vane 9 when the vane 9 is at the minimum stroke amount.
- the deep concave portion 36c and the shallow shallow portion 36d of the first concave portion 36 are formed on the rotor body 3a with respect to the first concave portion 36. It is divided by two boundary lines S5 and S6 extending along a straight line passing through both the axis P1 and the center P2 of the cylinder hole 6c.
- the depth in the axial direction of the drive shaft of the recessed deep portion 36c is shallow. The depth is greater than the axial depth of the drive shaft of the portion 36d.
- the communication area through which the lubricating oil passes through the first recess 36 is When the rear side block 6b side opening of the back pressure chamber 10 is within a range facing the concave shallow portion 36d of the first concave portion 36, the lubricating oil passes through the first concave portion 36.
- the communication area is relatively reduced.
- the point where the boundary line S5 and the inner peripheral surface of the cylinder hole 6c intersect is defined as X5.
- the point where the boundary line S6 intersects the inner peripheral surface of the cylinder hole 6c is X6, and the rotation direction of the rotor 3 is viewed from the front side of the vane compressor 1. In (a), it turns counterclockwise as shown by the arrow, and in the state seen from the rear side of the vane compressor 1, it turns clockwise as shown by the arrow in FIGS. 11 (c) and 12 (c).
- the vane 9 protrudes from the vane groove 8 beyond the outer surface of the rotor 3 as indicated by the thick arrow in FIG. 11B in the range where X5 is the start point and X6 is the end point.
- X6 is the starting point
- X5 is the ending point
- the enclosed, as shown in bold arrows in FIG. 12 (b), the stroke of the vane 9 is gradually retracted from the outer surface of the rotor 3 in the vane groove 8 is timing to decrease.
- a straight line connecting X5 and X6, which divides the timing when the stroke amount of the vane 9 increases or decreases, is the same as the boundary line S5 and the boundary line S6.
- the back pressure chamber 10 is supplied with the lubricating oil from the lubricating oil supply passages 33 and 34, but the second recess 37 has a back pressure chamber. 10 communicates with the concave portion 37d. Therefore, the communication area between the second recessed portion 37 and the back pressure chamber 10 is relatively reduced, and the first recessed portion 36 communicates with the back pressure chamber 10 at the recessed depth portion 36c. The communication area with the back pressure chamber 10 is relatively enlarged. For this reason, the back pressure chamber 10 has an arrow indicating the amount of lubricating oil from the lubricating oil supply passage 33 to the back pressure chamber 10 in FIG. 11B and the lubricating oil from the lubricating oil supply passage 34 to the back pressure chamber 10. As indicated by an arrow indicating the amount, the supply of lubricating oil is mainly received from the first recess 36.
- the second recess 37 communicates with the back pressure chamber 10 at the recess depth portion 37c when the lubricating oil is relatively raised and the lubricating oil is sent from the back pressure chamber 10 to the lubricating oil supply passages 33, 34, the second pressure is reduced.
- the communication area between the recess 37 and the back pressure chamber 10 is relatively Is enlarged, the first recess 36 is connected domain of the first recess 36 and the back pressure chamber 10 to communicates with the back pressure chamber 10 and the ⁇ site 36d is relatively reduced.
- the back pressure chamber 10 is indicated by an arrow indicating the amount of lubricating oil to the lubricating oil supply passage 33 and an arrow indicating the amount of lubricating oil to the lubricating oil supply passage 34 in FIG.
- the lubricating oil is mainly sent to the second recess 37.
- the flow rate of the lubricating oil sent from the back pressure chamber 10 to the lubricating oil supply passage 33 via the second recess 37 is the lubricating oil sent from the back pressure chamber 10 to the lubricating oil supply passage 34 via the first recess 36.
- the flow rate of the lubricating oil sent from the lubricating oil supply passage 33 through the second recess 37 to the back pressure chamber 10 is larger than the flow rate of the back pressure chamber 10 when viewed comprehensively.
- the flow rate of the lubricating oil sent to the lubricating oil supply passage 33 can be increased.
- FIGS. 13 and 14 show a third example of the second embodiment of the vane type compressor 1 in which the lubricating oil supply structure according to the present invention can be used.
- the first recess 36 shown in the third example of the second embodiment has the same configuration as the second example of the second embodiment described above, as shown in FIGS. 13 (a) and 14 (a).
- the first recess 36 shown in the second example of the second embodiment has a recessed deep portion 37c and a recessed shallow portion 37d. It does not have.
- symbol as the 2nd example of Example 2 is attached
- subjected the description is abbreviate
- the position of the second concave portion 37 where the second concave portion 37 is provided is the same as in the first and second examples of the second embodiment, and the description thereof is omitted.
- the second recess 37 has a circular line L1 constituting the circular opening edge of the drive shaft storage space 31 as an inner edge, and is concentric with the circular line L1.
- a circular line L6 is used as an outer edge, and the circular line L1 extends from the circular line L1 to the outer side in the radial direction of the drive shaft 2 with the same dimensions throughout the entire circumference.
- the dimension of the circular line L6 that forms the circumferential outer edge of the second recess 37 is, for example, substantially the same as the dimension of the bottom surface position of the vane 9 at the time of the minimum stroke amount of the vane 9.
- the second recess 37 is different from the first recess 36, and as shown in FIGS. 13A and 14A, the second recess 37 extends in the axial direction of the drive shaft in the entire region.
- the depth is the same.
- the depth dimension of the second recess 37 is the same as the axial depth of the drive shaft of the recess depth portion 36c of the first recess 36 in this third example.
- the point where the boundary line S5 and the inner peripheral surface of the cylinder hole 6c intersect is defined as X5, and the boundary line S6 and the inner periphery of the cylinder hole 6c.
- the point where the plane intersects is X6, and the rotation direction of the rotor 3 is opposite to that shown in the arrows in FIGS. 13 (a) and 14 (a) when viewed from the front side of the vane compressor 1.
- the starting point is X5.
- X6 is the end point, as shown by the thick arrow in FIG.
- the pressure in the back pressure chamber 10 is relatively lower than the lubricating oil supply passages 33 and 34, and the back pressure chamber 10 is supplied with the lubricating oil from the lubricating oil supply passages 33 and 34.
- the flow rate of the lubricating oil sent from the back pressure chamber 10 through the first recess 36 to the lubricating oil supply passage 34 is the lubricating oil sent from the lubricating oil supply passage 34 to the back pressure chamber 10 through the first recess 36. Therefore, it is possible to increase the flow rate of the lubricating oil sent from the back pressure chamber 10 to the lubricating oil supply passage 33 when viewed comprehensively.
- the lubricating oil supply structure according to the present invention has been described using the two-block vane compressor 1 in both the first and second embodiments.
- the two-block vane compressor 1 is not necessarily described.
- a vane type compressor may be used which is closed by being sandwiched between a front side block and a rear side block, and has a separate cylinder from these blocks.
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Abstract
Description
図7から図10では、この発明に係る潤滑オイル供給構造を用いることが可能なベーン型圧縮機1の実施例2の第1例が示されている。
図11及び図12では、この発明に係る潤滑オイル供給構造を用いることが可能なベーン型圧縮機1の実施例2の第2例が示されている。
図13及び図14では、この発明に係る潤滑オイル供給構造を用いることが可能なベーン型圧縮機1の実施例2の第3例が示されている。
2 駆動軸
3 ロータ
4 圧縮空間
5 ブロック
5a フロント側ブロック
5b シェル
6 ブロック
6a シリンダ
6b リア側ブロック
6c シリンダ孔
8 ベーン溝
9 ベーン
10 背圧室
12 プレーンベアリング
13 プレーンベアリング
16 吸入口
17 吐出口
19 オイル溜まり室
21 圧縮室
29 駆動軸収納空間
30 中継通路
31 駆動軸収納空間
33 潤滑オイル供給通路
34 潤滑オイル供給通路
36 第1の凹部
36a 連通状態形成用部位
36b 連通状態形成非対応部位
36c 凹深部位
36d 凹浅部位
37 第2の凹部
37a 連通状態形成用部位
37b 連通状態形成非対応部位
37c 凹深部位
37d 凹浅部位
Claims (8)
- 両側がブロックにより閉塞されたシリンダと、このシリンダ内に収納されると共に複数のベーン溝が形成されたロータと、このロータのベーン溝内に収納されて、側面が前記ベーン溝の内側面を摺動すると共に先端が前記ベーン溝から出没して前記シリンダの内周面を摺動するベーンと、前記ベーン溝の底部に形成された背圧室と、前記ブロックに各軸受を介して支持されると共に前記ロータと連結されて外部からの回転力を前記ロータに伝達する駆動軸と、潤滑オイルが一時的に溜められるオイル溜まり室とを有するベーン型圧縮機において、
潤滑オイルが、前記オイル溜まり室から前記駆動軸と前記ブロックのうちの一のブロックとの間に入り、前記駆動軸の軸方向に沿って流れて、その途中に位置する一方の軸受を潤滑した後、前記一のブロックのシリンダ側端面に形成された第1の凹部、前記背圧室、前記ブロックの他のブロックのシリンダ側端面に形成された第2の凹部の順に流れ、前記駆動軸と前記他のブロックとの間に入り、再度において前記駆動軸の軸方向に沿って流れて、その途中に位置する他方の軸受を潤滑する潤滑オイル経路を有し、
前記第1の凹部と前記第2の凹部とは、前記ロータの回転で前記背圧室の位置が変動することに伴い、それぞれ前記背圧室との連通状態を変化させることができると共に、前記ベーンの前記ロータのベーン溝からの突出量をベーンのストローク量とした場合に、この背圧室との連通状態の変化と前記ベーンのストローク量が増加していく時機とをリンクさせて、前記背圧室内の圧力を周囲よりも相対的に下げることにより、前記背圧室に潤滑オイルが供給されるようにしたことを特徴とするベーン型圧縮機の潤滑オイル供給構造。 - 前記第1の凹部と前記背圧室との間が開放される時機と、前記第2の凹部と前記背圧室との間が開放される時機とにずれを生じさせ、更に、この第1の凹部と前記背圧室との間及び前記第2の凹部と前記背圧室との間での開放時機のずれと前記ベーンのストローク量が増加していく時機とをリンクさせることにより、前記背圧室に潤滑オイルが供給されるようにしたことを特徴とする請求項1に記載のベーン型圧縮機の潤滑オイル供給構造。
- 前記ベーンのストローク量が増加していく時機と、前記第1の凹部と前記背圧室との間が前記第2の凹部と前記背圧室との間よりも早く開放される時機とを合わせたことを特徴とする請求項2に記載のベーン型圧縮機の潤滑オイル供給構造。
- 両側がブロックにより閉塞されたシリンダと、このシリンダ内に収納されると共に複数のベーン溝が形成されたロータと、このロータのベーン溝内に収納されて、側面が前記ベーン溝の内側面を摺動すると共に先端が前記ベーン溝から出没して前記シリンダの内周面を摺動するベーンと、前記ベーン溝の底部に形成された背圧室と、前記ブロックに各軸受を介して支持されると共に前記ロータと連結されて外部からの回転力を前記ロータに伝達する駆動軸と、潤滑オイルが一時的に溜められるオイル溜まり室とを有するベーン型圧縮機において、
潤滑オイルが、前記オイル溜まり室から前記駆動軸と前記ブロックのうちの一のブロックとの間に入り、前記駆動軸の軸方向に沿って流れて、その途中に位置する一方の軸受を潤滑した後、前記一のブロックのシリンダ側端面に形成された第1の凹部、前記背圧室、前記ブロックの他のブロックのシリンダ側端面に形成された第2の凹部の順に流れ、前記駆動軸と前記他のブロックとの間に入り、再度において前記駆動軸の軸方向に沿って流れて、その途中に位置する他方の軸受を潤滑する潤滑オイル経路を有し、
前記第1の凹部と前記第2の凹部とは、前記ロータの回転で前記背圧室の位置が変動することに伴い、それぞれ前記背圧室との連通状態を変化させることができると共に、前記ベーンの前記ロータのベーン溝からの突出量をベーンのストローク量とした場合に、この背圧室との連通状態の変化と前記ベーンのストローク量が減少していく時機とをリンクさせて、前記背圧室内の圧力を周囲よりも相対的に上げることにより、前記背圧室から潤滑オイルが送出されるようにしたことを特徴とするベーン型圧縮機の潤滑オイル供給構造。 - 前記第1の凹部と前記背圧室との間が閉塞される時機と、前記第2の凹部と前記背圧室との間が閉塞される時機とにずれを生じさせ、更に、この第1の凹部と前記背圧室との間及び前記第2の凹部と前記背圧室との間での閉塞時機のずれと前記ベーンのストローク量が減少していく時機とをリンクさせることにより、前記背圧室から潤滑オイルが送出されるようにしたことを特徴とする請求項4に記載のベーン型圧縮機の潤滑オイル供給構造。
- 前記ベーンのストローク量が減少していく時機と、前記第1の凹部と前記背圧室との間が前記第2の凹部と前記背圧室との間よりも早く閉塞される時機とを合わせたことを特徴とする請求項5に記載のベーン型圧縮機の潤滑オイル供給構造。
- 前記第1の凹部と前記第2の凹部との少なくとも一方を、前記ベーン型圧縮機の横幅方向において、前記駆動軸の軸方向における深度が相対的に深い部位と相対的に浅い部位とに区分けし、この深度の差異を利用して前記背圧室との連通状態を変化させることを特徴とする請求項1又は請求項4に記載のベーン型圧縮機の潤滑オイル供給構造。
- 前記第1の凹部又は第2の凹部であって前記駆動軸の軸方向における深度が相対的に深い部位と相対的に浅い部位とに区分けされない方の凹部は、その全域の深度が前記浅い部位と狭い部位とに区分けされた凹部の前記相対的に深い部位の深度と同じであることを特徴とする請求項7に記載のベーン型圧縮機の潤滑オイル供給構造。
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EP10840783.4A EP2520802A4 (en) | 2009-12-29 | 2010-12-28 | LUBRICATING OIL SUPPLY STRUCTURE FOR PALLET TYPE COMPRESSOR |
BR112012016134A BR112012016134A2 (pt) | 2009-12-29 | 2010-12-28 | estrutura de alimentação de óleo lubrificante de compressor do tipo de palhetas |
JP2011547336A JP5707337B2 (ja) | 2009-12-29 | 2010-12-28 | ベーン型圧縮機の潤滑オイル供給構造 |
CN2010800589514A CN102667162A (zh) | 2009-12-29 | 2010-12-28 | 叶片式压缩机的润滑油供给结构 |
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EP (1) | EP2520802A4 (ja) |
JP (1) | JP5707337B2 (ja) |
CN (1) | CN102667162A (ja) |
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Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
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JP2014001698A (ja) * | 2012-06-19 | 2014-01-09 | Toyota Industries Corp | ベーン型圧縮機 |
EP2803865A4 (en) * | 2011-12-21 | 2015-08-05 | Valeo Japan Co Ltd | COMPRESSOR WITH ELECTRIC MOTOR |
CN104948458A (zh) * | 2014-03-25 | 2015-09-30 | 株式会社丰田自动织机 | 叶片式压缩机 |
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CN107701447B (zh) * | 2017-09-29 | 2019-08-06 | 珠海格力电器股份有限公司 | 一种压缩机的油路结构和压缩机 |
CN109737065B (zh) | 2019-02-27 | 2024-04-16 | 珠海格力电器股份有限公司 | 泵体组件、压缩机及空调设备 |
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2010
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JPS61114092U (ja) * | 1984-12-28 | 1986-07-18 | ||
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Cited By (3)
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EP2803865A4 (en) * | 2011-12-21 | 2015-08-05 | Valeo Japan Co Ltd | COMPRESSOR WITH ELECTRIC MOTOR |
JP2014001698A (ja) * | 2012-06-19 | 2014-01-09 | Toyota Industries Corp | ベーン型圧縮機 |
CN104948458A (zh) * | 2014-03-25 | 2015-09-30 | 株式会社丰田自动织机 | 叶片式压缩机 |
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BR112012016134A2 (pt) | 2016-05-31 |
EP2520802A1 (en) | 2012-11-07 |
JP5707337B2 (ja) | 2015-04-30 |
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